JP2009052462A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase the reliability of a fixed scroll and a rotary scroll of a scroll compressor and also increase the efficiency of the scroll compressor by reducing leakage loss to match the compressor to recent refrigerating air conditioners increased in efficiency and life and using a high-pressure refrigerant such as carbon dioxide. <P>SOLUTION: A spiral seal member 80 is attached to a winding start part of the spiral lap end 12b of the fixed scroll 12. When the scroll compressor is under high load, the tooth bottom of the end plate 13a of the rotary scroll 13 and the winding start part of the lap end 12b of the fixed scroll 12 are deformed, and the winding start part of the fixed scroll 12 is heated and thermally expanded to the rotary scroll 13 side. However, since the seal member 80 is attached to the end of the winding start lap 12b of the fixed scroll 12, nonuniform contact does not occur, and high reliability can be realized. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in a cooling device such as a cooling / heating air conditioner or a refrigerator, or a heat pump type hot water supply device.

  Conventionally, in the scroll compressor, in order to keep the contact of the sliding surface between the orbiting and fixed end plates in a good state, improve the durability and reduce the leakage loss, about the wrap portion of the orbiting scroll or the fixed scroll, Based on the result of measuring the temperature distribution at the tip of the lap, the height dimension from the root of the end plate to the tip of the lap is adjusted, and in the assembled state, the height between each tip of the lap and the bottom of the other end plate The thrust direction gap that is the largest on the inner peripheral side is formed, or the thrust direction gap is changed in a plurality of stages (for example, see Patent Document 1).

FIG. 5 is a cross-sectional view of the orbiting scroll of the conventional scroll compressor described in Patent Document 1. As shown in FIG. 5, the lap portion tip 13d of the orbiting scroll 13 has an inner peripheral flat surface 13e and an outer peripheral flat surface 13f based on the result of measuring the temperature distribution during operation. The inclined surface between the side flat surface 13e and the outer peripheral side flat surface 13f is used to prevent galling due to the contact of the wrap tip portion 13d due to temperature rise and reduce leakage loss.
Japanese Patent Laid-Open No. 7-197891

  However, in the conventional configuration described in Patent Document 1, each compression chamber formed between the fixed scroll and the orbiting scroll is thermally expanded by the compression heat generated by the compression action. However, the deformation of the fixed scroll and the orbiting scroll due to the pressure difference between the discharge pressure and the suction pressure of the compressor is not taken into consideration.

  The orbiting scroll is deformed to the fixed scroll side due to the differential pressure between the discharge pressure and the suction pressure, and the center of the orbiting scroll is particularly configured when the back of the orbiting scroll is partitioned into a high pressure and an intermediate pressure by a sliding partition ring. Because of the deformation, the contact surface pressure increases due to the contact between the bottom of the end plate of the orbiting scroll and the winding start of the tip of the wrap portion of the fixed scroll, causing galling to each other, resulting in compression efficiency and durability as a compressor. Will fall.

  In particular, when carbon dioxide is used as the refrigerant, the pressure difference between the discharge pressure of the compressor and the suction pressure is about 7 to 10 times higher than the pressure difference of the refrigeration cycle of the conventional HFC refrigerant. There is a problem that deformation becomes easier to the side, galling occurs at the tooth bottom of the end plate of the orbiting scroll and the tip of the lap portion, and the compressor efficiency and durability as a compressor are reduced.

  In the conventional configuration, the height dimension from the tooth bottom of the end plate to the tip of the wrap is measured based on the result of measuring the temperature distribution at the tip of the wrap during high load operation for the orbiting scroll or fixed scroll. When adjusted, a gap is created at the tip of the lap portion during low-load operation, resulting in a reduction in compressor efficiency.

Therefore, the present invention has been made in view of the above-described conventional problems, and achieves high reliability even when there is pressure deformation of the orbiting scroll due to the differential pressure between the discharge pressure and the suction pressure at the time of high load. It aims at providing the scroll compressor which implement | achieves high efficiency in a driving | operation area | region.

  In order to solve the above-mentioned conventional problems, the scroll compressor according to the present invention is provided with a spiral seal member at the winding start portion at the tip of the wrap portion of the fixed scroll.

  With this configuration, during high loads, the orbiting scroll is deformed to the fixed scroll side due to the differential pressure between the discharge pressure and the suction pressure, and in particular, the bottom of the end plate of the orbiting scroll and the winding start portion at the tip of the fixed scroll wrap portion. Even when the deformation is large, since the seal member is provided at the leading end of the winding start portion of the fixed scroll, high reliability can be realized without causing a single contact.

  The scroll compressor of the present invention is highly reliable at the bottom of the end plate of the orbiting scroll and the tip of the fixed scroll lap portion, which are relatively slid even during high load operation where the pressure difference between the discharge pressure and the suction pressure is high. In addition, during low-load operation, the compressor efficiency can be improved by reducing the leakage loss due to the seal member, and the efficiency of the refrigeration and air-conditioning equipment can be improved.

  1st invention installs a spiral seal member in the winding start part of the lap | wrap part front-end | tip of a fixed scroll.

  As a result, during high loads, the orbiting scroll is deformed to the fixed scroll side due to the differential pressure between the discharge pressure and the suction pressure. In addition, the winding start portion of the fixed scroll becomes hot and thermally expands toward the orbiting scroll. However, since the seal member is provided at the tip of the winding start portion of the fixed scroll, it is highly reliable without hitting it. Can be realized.

  Further, at the time of low load operation, the compressor efficiency can be improved by reducing the leakage loss by the seal member, and high efficiency can be realized.

  The second invention is the first invention, in particular, in which the region where the seal member exists is substantially matched with the region where the inside of the housing portion of the bearing of the orbiting scroll turns. In the case where the end plate thickness of the orbiting scroll bearing housing is thinner than the outer peripheral portion thereof, the inner side of the bearing housing portion is particularly pressure-deformed toward the fixed scroll side. Since it is provided at the winding start portion of the fixed scroll corresponding to the region in which the inner side of the housing turns, high reliability can be realized without causing a single contact.

  The third invention is the first or second invention, in which the wrap height of the portion where the sealing member of the fixed scroll is installed is made lower than the other portions. As a result, even when the center portion of the bottom surface of the orbiting scroll is deformed to the fixed scroll side under a high load, the wrap tip of the fixed scroll provided with the seal member does not come into contact with the bottom surface of the orbiting scroll. Reliability can be realized.

  A fourth invention is any one of the first to third inventions, in which a spring member is disposed between the seal member storage groove and the seal member.

  As a result, the entire seal member is reliably pressed against the bottom surface of the end plate of the orbiting scroll, leakage in the compression chamber can be reduced, and a highly efficient scroll compressor can be realized in the entire operation region.

  The fifth invention is any one of the first to fourth inventions, and uses carbon dioxide as the working refrigerant.

  Since the carbon dioxide refrigerant is a high differential pressure refrigerant, an excessive pressing force is generated on the surface on which the end plate of the orbiting scroll and the end plate of the fixed scroll slide. It will cause abnormal wear. In particular, the orbiting scroll is more easily deformed to the fixed scroll side, causing galling at the bottom of the end plate of the orbiting scroll and the tip of the wrap portion of the fixed scroll, reducing the compressor efficiency and durability as a compressor. End up. When carbon dioxide refrigerant is used, the pressure difference between the discharge pressure and the suction pressure of the compressor is about 7 to 10 times higher than the pressure difference of the conventional refrigeration cycle using chlorofluorocarbon as a refrigerant. Furthermore, the performance was reduced. According to the first to fifth inventions, even when there is pressure deformation of the orbiting scroll due to the differential pressure between the discharge pressure and the suction pressure at the time of high load, the seal member is provided at the tip of the winding start portion of the fixed scroll. High reliability can be realized without doing so. Further, high efficiency can be realized in the entire operation region.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention, and FIG. 2 is a front view of a fixed scroll of the scroll compressor. The operation and action of the scroll compressor configured as shown in the figure will be described below.

  As shown in FIG. 1, the scroll compressor of the present invention includes a main bearing member 11 of a crankshaft 4 fixed by welding or shrink fitting in an airtight container 1, and a fixed bolted on the main bearing member 11. The scroll-type compression mechanism 2 is configured by sandwiching the orbiting scroll 13 that meshes with the fixed scroll 12 between the scroll 12 and prevents the orbiting scroll 13 from rotating between the orbiting scroll 13 and the main bearing member 11. By providing an anti-rotation mechanism 14 such as an Oldham ring that guides the orbit to move, the orbiting scroll 13 is eccentrically driven by the eccentric shaft portion 4a at the upper end of the crankshaft 4, thereby causing the orbiting scroll 13 to move in a circular orbit, Thereby, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 is small while moving from the outer peripheral side to the center portion. The refrigerant gas is sucked and compressed from the suction pipe 16 communicating with the outside of the hermetic container 1 and the suction port 17 on the outer peripheral portion of the fixed scroll 12, and the refrigerant gas exceeding the predetermined pressure is fixed. The reed valve 19 is pushed open from the discharge port 18 at the center of the scroll 12 and discharged into the sealed container 1 repeatedly.

  A sliding partition ring 78 disposed on the main bearing member 11 is provided on the back surface portion of the orbiting scroll 13, and the high pressure portion that is an inner region of the sliding partition ring 78 is formed by the sliding partition ring 78 while performing the orbiting motion. 30 and a back pressure space 29 set to an intermediate pressure of high pressure and low pressure, which is an outer region. By applying pressure on the back surface, the orbiting scroll 13 is stably pressed against the fixed scroll 12, reducing leakage and performing stable circular orbit movement.

  Further, the fixed scroll 12 includes a back pressure adjusting valve 9 that controls the pressure in the back pressure space 29 on the back surface of the orbiting scroll 13.

During operation of the compressor, a pump 25 is provided at the other downward end of the crankshaft 4 and is driven simultaneously with the scroll compressor. As a result, the pump 25 sucks up the oil 6 in the oil reservoir 20 provided at the bottom of the hermetic container 1 and vertically passes through the crankshaft 4.
To the compression mechanism 2. The supply pressure at this time is substantially equal to the discharge pressure of the scroll compressor, and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with each other, and the predetermined compression function is stably exhibited.

  A part of the oil 6 supplied in this way is obtained by a supply pressure or its own weight so as to obtain a clearance, between the fitting portion between the eccentric shaft portion 4a and the orbiting scroll 13, and between the crankshaft 4 and the main bearing member 11. Then, the oil enters the bearing portion 66, lubricates the respective portions, falls, and returns to the oil sump 20.

  Further, the oil 6 supplied to the high pressure portion 30 enters the back pressure space 29 around the outer peripheral portion of the orbiting scroll 13 where the rotation restricting mechanism 14 is located by the communication passage 54 provided in the orbiting scroll. The back pressure of the orbiting scroll 13 is applied in the back pressure space 29 in addition to lubricating the sliding portion by the meshing of the fixed scroll 12 and the orbiting scroll 13 and the sliding portion of the rotation restricting mechanism 14.

  The oil 6 entering the back pressure space 29 is set to an intermediate pressure that is intermediate between the pressures of the high pressure portion 30 and the low pressure side of the compression chamber 15 by the throttle action of the throttle 57. The back pressure space 29 is sealed between the high pressure portion 30 and the high pressure side by an annular partition ring 78. The pressure increases as the incoming oil is filled, and when the pressure exceeds a predetermined pressure, the back pressure adjusting valve 9 Acts to return to the suction portion of the compression chamber 15 and enter.

  The approach of the oil 6 is repeated at a predetermined cycle, and the timing of this repetition depends on the combination of the repetitive cycle of suction, compression, and discharge and the relationship between the pressure setting by the throttle hole 57 and the pressure setting by the back pressure adjusting mechanism 9. As a result, the sliding of the fixed scroll 12 and the wrap 13b of the orbiting scroll 13 is intentionally lubricated. This intentional lubrication is always ensured by the opening of the communication path 10 into the recess 105 by the back pressure regulating valve 9 as described above. The oil 6 supplied to the suction port 17 moves to the compression chamber 15 along with the orbiting motion of the orbiting scroll 13 and serves to prevent leakage between the compression chambers 15.

  Further, as shown in FIGS. 1 and 2, a spiral seal member 80 is provided at the winding start portion of the spiral wrap tip 12 b of the fixed scroll 12.

  With such a configuration, the orbiting scroll 13 is deformed to the fixed scroll 12 side due to the differential pressure between the discharge pressure and the suction pressure at a high load. In particular, the end plate 13a of the orbiting scroll 13 and the fixed scroll 12 are fixed. The deformation of the winding start portion at the tip of the wrap 12b increases, and the winding start portion of the fixed scroll 12 becomes hot and thermally expands toward the orbiting scroll 13, but at the tip of the winding start portion wrap 12b of the fixed scroll 12 Since the seal member 80 is provided, high reliability can be realized without causing a single contact.

  Further, at the time of low load operation, the compressor efficiency can be improved by reducing the leakage loss by the seal member 80, and high efficiency can be realized.

  In addition, as shown in FIG. 2, the region where the seal member 80 exists is substantially matched with the region where the inside of the bearing housing portion 13 c of the orbiting scroll 13 turns. As shown in FIG. 1, when the end plate thickness inside the housing 13c of the bearing of the orbiting scroll 13 is thinner than the outer peripheral portion, the end plate 13a inside the housing portion 13c of the bearing is particularly Although the pressure is deformed to the fixed scroll 12 side, the seal member 80 is provided at the winding start portion of the fixed scroll 12 corresponding to the region in which the inside of the housing 13c of the bearing of the orbiting scroll 13 is swiveled. High reliability can be realized.

(Embodiment 2)
In the scroll compressor according to the second embodiment of the present invention, the height of the wrap 12b in the portion where the seal member 80 of the fixed scroll 12 is installed is made lower than the other portions. FIG. 3 shows a cross-sectional view of the fixed scroll 12. The height of the wrap 12b at the portion where the seal member 80 of the fixed scroll 12 is installed is made lower by Δh than the other portions. As a result, even when the center of the bottom surface of the end plate 13a of the orbiting scroll 13 is deformed toward the fixed scroll 12 during a high load, the tip of the wrap 12b of the fixed scroll 12 provided with the seal member 80 is the end plate 13a of the orbiting scroll 13. High reliability can be achieved without contact with the bottom surface.

(Embodiment 3)
In the scroll compressor according to the third embodiment of the present invention, a spring member 85 is disposed between the seal member storage groove 81 and the seal member 80.

  FIG. 4 is an enlarged cross-sectional view of a main part of the wrap 12 b of the fixed scroll 12. As a result, the entire area of the seal member 80 is more reliably pressed against the orbiting scroll 13 by the spring force of the spring 85, leakage in the compression chamber 15 can be reduced, and a highly efficient scroll compressor can be realized. .

(Embodiment 4)
The scroll compressor according to the fourth embodiment of the present invention uses carbon dioxide as a working refrigerant. Since the carbon dioxide refrigerant is a high differential pressure refrigerant, an excessive pressing force is generated on the surface on which the end plate 13a of the orbiting scroll 13 and the tip of the wrap 12b of the fixed scroll 12 slide, which increases the sliding loss. Or it will cause galling and abnormal wear. In particular, the orbiting scroll 13 is more easily deformed toward the fixed scroll 12, and galling occurs at the bottom of the end plate 13 a of the orbiting scroll 13 and the tip of the wrap 12 b of the fixed scroll 12, so that the compressor efficiency and durability as a compressor are increased. The nature will decline. When carbon dioxide refrigerant is used, the pressure difference between the discharge pressure and the suction pressure of the compressor is about 7 to 10 times higher than the pressure difference of the conventional refrigeration cycle using chlorofluorocarbon as a refrigerant. Furthermore, the performance was reduced. According to the first to third embodiments of the present invention, even when there is a pressure deformation of the orbiting scroll 13 due to a differential pressure between the discharge pressure and the suction pressure at a high load, a seal is provided at the leading end of the wrap 12b winding start portion of the fixed scroll 12. Since the member 80 is provided, high reliability can be realized without hitting one piece. Further, high efficiency can be realized in the entire operation region.

  As described above, the scroll compressor according to the present invention can improve the compression efficiency even under high differential pressure operation, and the air scroll compressor, the vacuum pump, the scroll type expansion can be realized without limiting the working fluid to the refrigerant. It can also be applied to the use of scroll fluid machines such as machines.

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention The front view of the fixed scroll of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the fixed scroll of the scroll compressor in Embodiment 2 of this invention Sectional drawing of the wrap part of the fixed scroll of the scroll compressor in Embodiment 3 of this invention Sectional view of the orbiting scroll of a conventional scroll compressor

Explanation of symbols

6 Oil 11 Main bearing member 12 Fixed scroll 12a End plate 12b Wrap 13 Orbiting scroll 13a End plate 13b Wrap 13c Housing portion 14 Rotation restricting mechanism 15 Compression chamber 17 Suction port 29 Back pressure space 30 High pressure portion 31 High pressure space 78 Sliding partition ring 80 Seal Member 81 Seal member storing groove 85 Spring

Claims (5)

By engaging the fixed scroll where the spiral wrap rises from the end plate and the orbiting scroll, and moving the orbiting scroll along a circular orbit under the regulation of rotation, it moves while changing the volume, so that suction, compression, A compression chamber for discharging is formed, and a ring-shaped groove is provided in a bearing member that substantially supports the orbiting scroll and the back side of the end plate, and a high pressure is applied to the bearing member and the central part on the back side of the end plate by lubricating oil. The high pressure portion to be applied and the high pressure portion are partitioned by a ring-shaped sliding partition ring having a joint portion attached to the groove portion, and a predetermined pressure lower than that of the high pressure portion is applied to the outer peripheral portion of the rear surface of the orbiting scroll end plate In the scroll compressor provided with a back pressure space, a spiral seal member is installed at the winding start portion at the tip of the wrap portion of the fixed scroll. Scroll compressor. The scroll compressor according to claim 1, wherein the region where the seal member exists is made to substantially coincide with a region where the inside of the housing portion of the bearing of the orbiting scroll turns. The scroll compressor according to claim 1 or 2, wherein a wrap height of a portion where the sealing member of the fixed scroll is installed is made lower than that of other portions. The scroll compressor according to any one of claims 1 to 3, wherein a spring member is disposed between the seal member and the seal member storage groove. The scroll compressor according to any one of claims 1 to 4, wherein carbon dioxide is used as a working refrigerant.

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